EP0450646B1 - Double plate gate valve - Google Patents
Double plate gate valve Download PDFInfo
- Publication number
- EP0450646B1 EP0450646B1 EP91105416A EP91105416A EP0450646B1 EP 0450646 B1 EP0450646 B1 EP 0450646B1 EP 91105416 A EP91105416 A EP 91105416A EP 91105416 A EP91105416 A EP 91105416A EP 0450646 B1 EP0450646 B1 EP 0450646B1
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- EP
- European Patent Office
- Prior art keywords
- slide valve
- sealing rings
- tube portion
- sealing
- slide
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
- F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
- F16K3/16—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with special arrangements for separating the sealing faces or for pressing them together
- F16K3/18—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with special arrangements for separating the sealing faces or for pressing them together by movement of the closure members
- F16K3/184—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with special arrangements for separating the sealing faces or for pressing them together by movement of the closure members by means of cams
Definitions
- the invention relates to a double-plate slide valve according to the preamble of claim 1 and 7.
- Gate valves of this type are generally known and have been manufactured and sold by the applicant for years (see prospectus No. 300, II / 82 of the applicant with the title "fittings and equipment for processes in refineries, petrochemicals, chemistry - program III; as well as DE-U-80 08 316).
- Pipe bridge slides as flat, oval and round slides are available both in the form of single-plate slides and in the form of double-plate slides (wedge in the wedge Principle), namely with a rising spindle and a straight, tubular passage in the open position. In the present case, it is about the further development of a tube bridge valve in the manner of a double-plate valve.
- Such valves are used when the flow chamber is sealed against the valve in the open position the remaining housing interior is required. This is particularly the case if it is a gas flow with contaminants from subliming substances, because otherwise they accumulate in unclosed housing parts and can lead to total blockage and thus to prevention of slide actuation.
- Such sliders are also used for similar reasons in dusty gases but also heavily contaminated liquid media, e.g. B. in coal gasification plants, incineration plants, chemical plants, pipelines or the like.
- a double-plate slide valve has become known, the tube bridge of which is composed of an elastic corrugated tube with sliding and sealing rings arranged on the end face.
- the pipe bridge is housed in a tubular housing part of the slide plate, which is also used to hold and guide the pipe bridge.
- the slide rings are pressed against the housing sealing seats by the elasticity of the corrugated tube and by the expansion effect of a wedge device.
- This known construction has the disadvantage that the prestress of the elastic corrugated tube must be set relatively high in order to achieve a sufficiently high tightness. The result is that when the pipe bridge is moved, the sealing rings slide along the opposite sealing seats of the valve housing with a relatively large contact pressure.
- the pipe bridge is composed of two sealing rings and a compensator that connects the sealing rings.
- the sealing rings are dimensioned so that their diameter matches that of the housing sealing seats.
- the compensator consists of an elastic, wavy, bent sheet metal ring, which is installed in such a way that dirt deposits are blown away by itself when the compensator is compressed or pressed apart.
- the sealing rings are spread out by means of a wedge device which has two housing parts which are stationary and arranged laterally in the slide housing and which cooperate with two plate wedges attached to the sealing rings in the open position of the slide.
- the pipe bridge also has a return device, each with four rollers, which are attached to the sealing rings laterally and in pairs symmetrically to their central axis.
- the rollers run on four actuating strips in the valve housing, which are provided with inlet grooves for the rollers in the area of the slide passage.
- the shut-off plates also each have four rollers that run on the actuating strips mentioned above.
- the clear width between the actuating strips and the groove depth of the inlet grooves are dimensioned such that both the shut-off plates and the sealing rings of the pipe bridge are pressed gas-tight against the housing sealing seats by the inner wedge or the housing wedges in the closed position or in the open position of the slide, while they are guided outside these two switch positions at a distance from the housing sealing seats.
- the sealing rings are either pressed against the sealing seats of the valve housing by mechanical means (wedge mechanism, rollers, inlet grooves, actuating strips) and mechanical positive control or are lifted off them , depending on the slide position.
- the aforementioned forced mechanism means that adaptation to changed external conditions, in particular to different pressures within the pipeline in which the slide is installed, is not possible.
- the known double-slide valve construction - as already explained above - is required by a large number of components which are coordinated with one another with regard to the movement sequence and which result in a high expenditure of material as well as production and assembly costs. Accordingly, maintenance is also complex.
- the present invention is based on the object of developing a double-plate slide valve of the type mentioned in such a way that, with a reduced number of components, an unchanged high level of tightness between the sealing rings of the pipe bridge and the associated sealing seats of the slide valve housing is ensured when the slide valve is open, while at the same time being well adapted to changed external conditions, in particular different pressures in the slide passage, should be possible.
- a higher gas pressure is set within the valve housing than in the pipeline or in the valve passage. This pressure acts on the circumferential indentation or on the sealing ring and pipe section surfaces in such a way that the sealing rings of the pipe bridge are pressed against the associated sealing seats with a corresponding sealing of the slide housing with respect to the slide passage or the pipe in the slide open position.
- the pressure in the valve body is adjusted according to the pressure prevailing in the valve passage. Flushing steam, which is present anyway for cleaning the slide, is preferably used as the pressure medium.
- valve housing is under increased flushing vapor pressure compared to the valve passage or the pipeline also prevents or reduces to a minimum the accumulation of dirt or other gaseous or liquid media flowing through the pipeline in the valve housing. Accordingly, the flushing steam consumption for cleaning purposes is minimal in the constructions according to the invention.
- the above-mentioned pressure setting in the slide housing also ensures a high level of tightness between the tube bridge and the slide housing in the slide open position without excessive friction forces having to be overcome when the slide is actuated, specifically because the axial spreading of the sealing rings due to the gas pressure in the slide housing external conditions, in particular the pressure within the pipeline or within the slide passage is adjustable.
- the sealing effect of the compensator designed according to the invention can be reinforced by a compensator preload, provided that this should be expedient for a special use of the slide.
- 1 and 2 has a slide housing 11 with two pipe sockets 12 and 13 and two housing sealing seats 14 and 15, between which a slide plate 16, consisting of two shut-off plates 17, 18 with sealing rings 19, 20, is displaceable .
- the two shut-off plates 17 and 18 can be pressed against the housing sealing seats 14 and 15 with the aid of an inner wedge 21 which acts as an expansion element and which sits at the end of an actuating rod 22 and is firmly connected to the latter.
- the shut-off plates 17 and 18 can be expanded by the inner wedge 21 in a manner known per se according to the so-called "wedge in the wedge principle".
- a pipe bridge 23, which is composed of two sealing rings 24, 25 and a compensator 26 connecting the sealing rings to one another, is arranged below or next to the slide plate 16.
- the compensator 26 consists of an inner pipe section 27 and an outer pipe section 28 which extends coaxially thereto, the outer pipe section 28 being fixedly connected to both sealing rings 24, 25, namely welded (ring weld seams 29, 30) and a shaft extending over the circumference or indentation 31.
- the inner tube section 27, on the other hand, is hollow-cylindrical, that is to say without a corrugation, so that no flow losses resulting therefrom occur. Furthermore, the inner tube section is only firmly connected to one of the two sealing rings, namely here the sealing ring 25 (ring weld seam 32).
- the inner tube section 27 is axially movable, wherein the axial play between the sealing ring 24 and the inner tube section 27 is between about 1.0 mm to about 5.0 mm.
- the arrangement of the inner pipe section 26 relative to the two sealing rings 24 and 25 is such that the inner surface of the pipe section 26 is aligned with the inner surfaces of the sealing rings 24 and 25, so that a practically uninterrupted flow passage is created in the open position of the slide. 1 and 2, the slide is shown in the closed position.
- the slide housing 11 is designed to be fluid-tight towards the outside, so that a gas pressure which is greater than the pressure in the slide passage or in the pipeline not shown in FIGS. 1 and 2 when the slide is open can be set within the slide housing or in the interior 33 thereof .
- connection 34 for connection to a pressure gas source is arranged on the slide housing 11.
- a pressure gas source not shown, in particular purging steam source
- the sealing surfaces of the sealing rings 24, 25 on the one hand and housing sealing seats 14, 15 on the other hand each extend parallel to the slide actuation direction, hardened or armored in a manner known per se in order to increase the wear resistance increase.
- the circumferential indentation 31 of the outer tube section 28 extends close to the outer surface of the inner tube section 27, so that the gas pressure prevailing in the housing interior 33 is fully effective via the circumferential indentation 31 on the sealing rings 24, 25 with the axial expansion of the same.
- the axial expansion of the sealing rings 24, 25 is possible on the one hand by the circumferential indentation 31 and on the other hand by the axial play between the inner tube section 27 and one of the two sealing rings, here sealing ring 24.
- the pipe bridge 23 is accordingly limited by the two sealing rings 24, 25 on the one hand and the inner and outer pipe sections 27, 28 arranged between them and serving as compensators 26 on the other hand, forming an annular box 35.
- This ring box 35 or the annular space between the inner and outer tube sections 27 and 28 is filled with a heat-insulating material, in particular glass wool, rock wool, or the like.
- This filling not only has a heat-insulating purpose, but also the purpose of preventing the penetration of flow medium into the said annular space between the inner and outer pipe section. A clogging of the annular space with flow medium or with gas flow with dust and dirt particles or the like. Deposits would impair or impair the effect of the compensator 26 after prolonged use. In this respect, the aforementioned filling has a double function.
- an adjustable pressure relief valve to the slide housing 11 or the interior 33 thereof in order not to exceed a predetermined pressure in the interior 33 of the slide housing 11, this pressure being set such that it provides a sufficiently high level of sealing security between the sealing rings 24, 25 on the one hand and the associated housing sealing seats 14, 15 of the slide housing, on the other hand, are guaranteed when the slide is open.
Abstract
Description
Die Erfindung betrifft einen Doppelplatten schieber gemäß dem Oberbegriff des Anspruches 1 bzw. 7. Absperrschieber dieser Art sind allgemein bekannt und werden von der Anmelderin seit Jahren hergestellt und vertrieben (s. Prospekt Nr. 300, II/82 der Anmelderin mit dem Titel "Armaturen und Einrichtungen für Prozesse in Raffinerien, Petrochemie, Chemie - Programm III; sowie DE-U-80 08 316). Rohrbrückenschieber als Flach-, Oval- und Rundschieber sind sowohl in Form von Einplattenschieber als auch in Form von Doppelplattenschieber (Keil im Keil-Prinzip) bekannt, und zwar mit steigender Spindel und geradem, rohrförmigem Durchgang in Offenstellung. Im vorliegenden Fall geht es um die Weiterentwicklung eines Rohrbrückenschiebers nach Art eines Doppelplattenschiebers. Derartige Schieber kommen dann zur Anwendung, wenn in der Offenstellung des Schiebers eine Abdichtung seines Durchflußraumes gegenüber dem übrigen Gehäuseinnenraum verlangt wird. Dies ist insbesondere der Fall, wenn es sich um einen Gasstrom mit Verunreinigungen aus sublimierenden Stoffen handelt, weil diese sonst sich in nichtabgeschlossenen Gehäuseteilen anlagern und zu einer Totalverstopfung und somit zu einer Verhinderung der Schieberbetätigung führen können. Derartige Schieber werden auch aus ähnlichen Gründen bei staubhaltigen Gasen aber auch stark verschmutzten flüssigen Medien eingesetzt, z. B. in Kohlevergasungsanlagen, Verbrennungsanlagen, chemischen Anlagen, Pipelines oder dgl.The invention relates to a double-plate slide valve according to the preamble of claim 1 and 7. Gate valves of this type are generally known and have been manufactured and sold by the applicant for years (see prospectus No. 300, II / 82 of the applicant with the title "fittings and equipment for processes in refineries, petrochemicals, chemistry - program III; as well as DE-U-80 08 316). Pipe bridge slides as flat, oval and round slides are available both in the form of single-plate slides and in the form of double-plate slides (wedge in the wedge Principle), namely with a rising spindle and a straight, tubular passage in the open position. In the present case, it is about the further development of a tube bridge valve in the manner of a double-plate valve. Such valves are used when the flow chamber is sealed against the valve in the open position the remaining housing interior is required. This is particularly the case if it is a gas flow with contaminants from subliming substances, because otherwise they accumulate in unclosed housing parts and can lead to total blockage and thus to prevention of slide actuation. Such sliders are also used for similar reasons in dusty gases but also heavily contaminated liquid media, e.g. B. in coal gasification plants, incineration plants, chemical plants, pipelines or the like.
Aus der DE-C-868 543 ist ein Doppelplattenschieber bekannt geworden, dessen Rohrbrücke sich aus einem elastischen Wellrohr mit stirnseitig angeordneten Gleit- und Dichtringen zusammensetzt. Die Rohrbrücke ist in einem rohrförmigen Gehäuseteil der Schieberplatte untergebracht, welches gleichzeitig zur Halterung und Führung der Rohrbrücke dient. In der Offenstellung des Schiebers werden die Gleitringe gegen die Gehäusedichtsitze durch die Elastizität des Wellrohres sowie durch die Spreizwirkung einer Keilvorrichtung angepreßt. Diese bekannte Konstruktion hat den Nachteil, daß zur Erzielung einer ausreichend hohen Dichtigkeit die Vorspannung des elastischen Wellrohres relativ hoch eingestellt sein muß. Die Folge ist, daß beim Verschieben der Rohrbrücke deren Dichtringe mit einer relativ großen Anpreßkraft an den gegenüberliegenden Dichtsitzen des Schiebergehäuses entlanggleiten. Dadurch entsteht eine beträchtliche Reibung zwischen den anliegenden Dichtflächen, so daß erhebliche Betätigungskräfte zum Umschalten des Schiebers erforderlich sind. Zur Vermeidung dieser Nachteile wird im DE-U-80 08 316 vorgeschlagen, die Dichtringe der Rohrbrücke an einer Verlängerung der Betätigungsstange für die Schieberplatte aufzuhängen und mit einer Rückstellvorrichtung zu versehen, die an den Dichtringen befestigte Rollen aufweist, welche auf im Gehäuse angebrachten Betätigungsleisten mit im Bereich des Schieberdurchganges angeordneten Einlaufnuten für die Rollen laufen. Diese kombinierte Spreiz- und Lösevorrichtung soll zum einen eine sichere Anpressung der Dichtringe in der Offenstellung des Schiebers und zum anderen die freie Beweglichkeit der Rohrbrücke entlang der beiden Gehäusedichtsitze beim Betätigen des Schiebers gewährleisten. Zusätzlich wird noch vorgeschlagen, auch die Absperrplatten der Schieberplatte mit Rollen zu versehen, die in Schließstellung in die Einlaufnuten der Betätigungsleisten laufen, um, vor allem bei hohen Differenzdrücken, ein Verschieben der Absperrplatten mit geringstmöglicher Reibung und ohne Beschädigung der Dichtflächen zu ermöglichen. Konkret ist die Rohrbrücke aus zwei Dichtringen sowie einem die Dichtringe miteinander verbindenden Kompensator zusammengesetzt. Die Dichtringe sind so bemessen, daß ihr Durchmesser mit dem der Gehäusedichtsitze übereinstimmt. Der Kompensator besteht aus einem elastischen, wellig gebogenen Blechring, der so eingebaut ist, daß Schmutzablagerungen von selbst weggesprengt werden, wenn der Kompensator zusammengedrückt oder auseinandergedrückt wird. Die Dichtringe werden in der Offenstellung des Schiebers mittels einer Keilvorrichtung aufgespreizt, die zwei im Schiebergehäuse ortsfest und seitlich angeordnete Gehäuseteile aufweist, welche in der Offenstellung des Schiebers mit je zwei an den Dichtringen angebrachten Plattenkeilen zusammenwirken. Die Rohrbrücke weist ferner eine Rückstellvorrichtung mit je vier Rollen auf, die an den Dichtringen seitlich und paarweise symmetrisch zu deren Mittelachse befestigt sind. Die Rollen laufen auf vier im Schiebergehäuse angebrachten Betätigungsleisten, welche im Bereich des Schieberdurchganges mit Einlaufnuten für die Rollen versehen sind. Auch die Absperrplatten weisen je vier Rollen auf, die auf den vorgenannten Betätigungsleisten laufen. Die lichte Weite zwischen den Betätigungsleisten und die Nuttiefe der Einlaufnuten sind so bemessen, daß sowohl die Absperrplatten als auch die Dichtringe der Rohrbrücke in der Schließstellung bzw. in der Offenstellung des Schiebers durch den Innenkeil bzw. die Gehäusekeile gasdicht gegen die Gehäusedichtsitze angepreßt sind, während sie außerhalb dieser beiden Schaltstellungen in einem Abstand von den Gehäusedichtsitzen geführt werden. Die vorgenannte Beschreibung der bekannten Konstruktion läßt erkennen, daß es sich um eine relativ aufwendige Konstruktion handelt. Viele einzelne Bauteile müssen hinsichtlich ihres Bewegungsablaufes aufeinander abgestimmt werden. Bei der Herstellung des bekannten Doppelplattenschiebers mit Rohrbrücke ist daher höchste Präzision gefordert. Des weiteren beinhaltet die bekannte Konstruktion eine Vielzahl von Verschleißteilen sowie Teilen, die einer gesonderten Reinigung nach vorbestimmter Gebrauchsdauer bedürfen. Zusammenfassend kann also festgehalten werden, daß bei dem bekannten Doppelplattenschieber mit Rohrbrücke gemäß DE-U-80 06 316 die Dichtringe durch mechanische Mittel (Keilmechanismus, Rollen, Einlaufnuten, Betätigungsleisten) sowie mechanische Zwangssteuerung entweder gegen die Dichtsitze des Schiebergehäuses gepreßt oder von diesen abgehoben werden, und zwar je nach Schieberstellung. Durch den vorgenannten Zwangsmechanismus ist eine Anpassung an veränderte äußere Bedingungen, insbesondere an unterschiedliche Drücke innerhalb der Rohrleitung, in welcher der Schieber eingebaut ist, nicht möglich. Des weiteren ist die bekannte Doppelplattenschieber-Konstruktion - wie bereits oben dargelegt - durch eine Vielzahl von hinsichtlich des Bewegungsablaufes aufeinander abgestimmten Bauteilen erforderlich, die sowohl einen hohen Materialaufwand als auch Fertigungs- und Montageaufwand zur Folge haben. Auch die Wartung ist dementsprechend aufwendig.From DE-C-868 543 a double-plate slide valve has become known, the tube bridge of which is composed of an elastic corrugated tube with sliding and sealing rings arranged on the end face. The pipe bridge is housed in a tubular housing part of the slide plate, which is also used to hold and guide the pipe bridge. In the open position of the slide, the slide rings are pressed against the housing sealing seats by the elasticity of the corrugated tube and by the expansion effect of a wedge device. This known construction has the disadvantage that the prestress of the elastic corrugated tube must be set relatively high in order to achieve a sufficiently high tightness. The result is that when the pipe bridge is moved, the sealing rings slide along the opposite sealing seats of the valve housing with a relatively large contact pressure. This creates considerable friction between the adjacent sealing surfaces, so that considerable actuation forces are required to switch the slide. To avoid these disadvantages, it is proposed in DE-U-80 08 316 to hang the sealing rings of the pipe bridge on an extension of the actuating rod for the slide plate and to provide them with a resetting device which has rollers attached to the sealing rings, which have actuating strips attached to the housing Run in the grooves arranged in the slide passage for the rollers. This combined spreading and loosening device On the one hand, it should ensure that the sealing rings are pressed securely in the open position of the slide and, on the other hand, that the pipe bridge can move freely along the two housing sealing seats when the slide is actuated. In addition, it is also proposed to provide the shut-off plates of the slide plate with rollers, which run in the closed position in the inlet grooves of the actuating strips, in order to enable displacement of the shut-off plates with the least possible friction and without damaging the sealing surfaces, especially at high differential pressures. Specifically, the pipe bridge is composed of two sealing rings and a compensator that connects the sealing rings. The sealing rings are dimensioned so that their diameter matches that of the housing sealing seats. The compensator consists of an elastic, wavy, bent sheet metal ring, which is installed in such a way that dirt deposits are blown away by itself when the compensator is compressed or pressed apart. In the open position of the slide, the sealing rings are spread out by means of a wedge device which has two housing parts which are stationary and arranged laterally in the slide housing and which cooperate with two plate wedges attached to the sealing rings in the open position of the slide. The pipe bridge also has a return device, each with four rollers, which are attached to the sealing rings laterally and in pairs symmetrically to their central axis. The rollers run on four actuating strips in the valve housing, which are provided with inlet grooves for the rollers in the area of the slide passage. The shut-off plates also each have four rollers that run on the actuating strips mentioned above. The clear width between the actuating strips and the groove depth of the inlet grooves are dimensioned such that both the shut-off plates and the sealing rings of the pipe bridge are pressed gas-tight against the housing sealing seats by the inner wedge or the housing wedges in the closed position or in the open position of the slide, while they are guided outside these two switch positions at a distance from the housing sealing seats. The above description of the known construction shows that it is a relatively complex construction. Many individual components must be coordinated with one another with regard to their movement sequence. The highest precision is therefore required in the manufacture of the well-known double-plate gate valve with a pipe bridge. Furthermore, the known construction includes a large number of wearing parts and parts which require separate cleaning after a predetermined period of use. In summary, it can be stated that in the known double-plate slide valve with a pipe bridge according to DE-U-80 06 316, the sealing rings are either pressed against the sealing seats of the valve housing by mechanical means (wedge mechanism, rollers, inlet grooves, actuating strips) and mechanical positive control or are lifted off them , depending on the slide position. The aforementioned forced mechanism means that adaptation to changed external conditions, in particular to different pressures within the pipeline in which the slide is installed, is not possible. Furthermore, the known double-slide valve construction - as already explained above - is required by a large number of components which are coordinated with one another with regard to the movement sequence and which result in a high expenditure of material as well as production and assembly costs. Accordingly, maintenance is also complex.
Der vorliegenden Erfindung liegt nun die Aufgabe zugrunde, einen Doppelplattenschieber der genannten Art so weiterzubilden, daß mit einer reduzierten Anzahl von Bauteilen eine unverändert hohe Dichtigkeit zwischen den Dichtringen der Rohrbrücke und den zugeordneten Dichtsitzen des Schiebergehäuses bei Schieberoffenstellung gewährleistet ist, wobei gleichzeitig eine gute Anpassung an veränderte äußere Bedingungen, insbesondere unterschiedliche Drücke im Schieberdurchgang, möglich sein sollen.The present invention is based on the object of developing a double-plate slide valve of the type mentioned in such a way that, with a reduced number of components, an unchanged high level of tightness between the sealing rings of the pipe bridge and the associated sealing seats of the slide valve housing is ensured when the slide valve is open, while at the same time being well adapted to changed external conditions, in particular different pressures in the slide passage, should be possible.
Diese Aufgabe wird erfindungsgemäß durch die kennzeichnenden Merkmale des Anspruches 1 oder 7 gelöst. Im Rahmen der erfindungsgemäßen Konstruktion wird innerhalb des Schiebergehäuses ein höherer Gasdruck eingestellt als in der Rohrleitung bzw. im Schieberdurchgang herrscht. Dieser Druck wirkt auf die umlaufende Einbuchtung bzw. auf die Dichtring- und Rohrabschnittflächen derart, daß die Dichtringe der Rohrbrücke gegen die zugeordneten Dichtsitze gepreßt wird unter entsprechender Abdichtung des Schiebergehäuses gegenüber dem Schieberdurchgang bzw. der Rohrleitung in Schieberoffenstellung. Entsprechend dem im Schieberdurchgang herrschenden Druck wird der Druck im Schiebergehäuse eingestellt. Vorzugsweise wird als Druckmedium Spüldampf verwendet, der ohnehin zur Reinigung des Schiebers vorhanden ist. Dadurch, daß das Schiebergehäuse unter gegenüber dem Schieberdurchgang bzw. der Rohrleitung erhöhtem Spüldampf-Druck steht, wird auch die Ablagerung von Schmutz oder anderen gasförmigen oder flüssigen Medien, die durch die Rohrleitung strömen, im Schiebergehäuse verhindert bzw. auf ein Minimum reduziert. Dementsprechend ist bei den erfindungsgemäßen Konstruktionen der Spüldampfverbrauch zu Reinigungszwecken minimal. Durch die vorgenannte Druckeinstellung im Schiebergehäuse ist auch stets eine hohe Dichtigkeit zwischen Rohrbrücke und Schiebergehäuse in Schieberoffenstellung gewährleistet, ohne daß zu große Reibungskräfte bei der Schieberbetätigung zu überwinden sind, und zwar dadurch bedingt, daß die axiale Spreizung der Dichtringe durch den Gasdruck im Schiebergehäuse an die äußeren Bedingungen, insbesondere den Druck innerhalb der Rohrleitung bzw. innerhalb des Schieberdurchgangs anpaßbar ist. Die Dichtwirkung des erfindungsgemäß ausgebildeten Kompensators kann noch durch eine Kompensator-Vorspannung verstärkt werden, sofern dies für einen speziellen Einsatz des Schiebers zweckmäßig sein sollte.This object is achieved by the characterizing features of claim 1 or 7. Within the framework of the construction according to the invention, a higher gas pressure is set within the valve housing than in the pipeline or in the valve passage. This pressure acts on the circumferential indentation or on the sealing ring and pipe section surfaces in such a way that the sealing rings of the pipe bridge are pressed against the associated sealing seats with a corresponding sealing of the slide housing with respect to the slide passage or the pipe in the slide open position. The pressure in the valve body is adjusted according to the pressure prevailing in the valve passage. Flushing steam, which is present anyway for cleaning the slide, is preferably used as the pressure medium. The fact that the valve housing is under increased flushing vapor pressure compared to the valve passage or the pipeline also prevents or reduces to a minimum the accumulation of dirt or other gaseous or liquid media flowing through the pipeline in the valve housing. Accordingly, the flushing steam consumption for cleaning purposes is minimal in the constructions according to the invention. The above-mentioned pressure setting in the slide housing also ensures a high level of tightness between the tube bridge and the slide housing in the slide open position without excessive friction forces having to be overcome when the slide is actuated, specifically because the axial spreading of the sealing rings due to the gas pressure in the slide housing external conditions, in particular the pressure within the pipeline or within the slide passage is adjustable. The sealing effect of the compensator designed according to the invention can be reinforced by a compensator preload, provided that this should be expedient for a special use of the slide.
Vorteilhafte Details der erfindungsgemäßen Schieberkonstruktion sind in den Unteransprüchen beschrieben, auf die hiermit Bezug genommen wird.Advantageous details of the slide construction according to the invention are described in the subclaims, to which reference is hereby made.
Nachstehend werden Ausführungsformen eines erfindungsgemäß ausgebildeten Doppelplattenschiebers mit Rohrbrücke anhand der beigefügten Zeichnung näher erläutert. Es zeigen:
- Fig. 1
- eine Teilansicht eines Doppelplattenschiebers mit Rohrbrücke, mit zum Teil weggebrochener Gehäusewand;
- Fig. 2
- den Doppelplattenschieber gemäß Fig. 1 im Schnitt längs Linie II-II in Fig. 1;
- Fig. 3
- eine Teilschnittansicht einer alternativen Ausführungsform einer Rohrbrücke;
- Fig. 4
- eine Teilschnittansicht einer weiteren alternativen Ausführungsform für eine Rohrbrücke.
- Fig. 1
- a partial view of a double-plate gate valve with a pipe bridge, with the housing wall broken away in part;
- Fig. 2
- 1 in section along line II-II in Fig. 1;
- Fig. 3
- a partial sectional view of an alternative embodiment of a pipe bridge;
- Fig. 4
- a partial sectional view of a further alternative embodiment for a pipe bridge.
Der in den Fig. 1 und 2 dargestellte Doppelplattenschieber 10 weist ein Schiebergehäuse 11 mit zwei Rohrstutzen 12 und 13 sowie zwei Gehäusedichtsitzen 14 und 15 auf, zwischen welchen eine Schieberplatte 16, bestehend aus zwei Absperrplatten 17, 18 mit Dichtringen 19, 20, verschiebbar ist. Die beiden Absperrplatten 17 und 18 sind gegen die Gehäusedichtsitze 14 und 15 mit Hilfe eines als Spreizorgan wirkenden Innenkeils 21 andrückbar, welcher am Ende einer Betätigungsstange 22 sitzt und mit dieser fest verbunden ist. Die Absperrplatten 17 und 18 sind durch den Innenkeil 21 in an sich bekannter Weise nach dem sogenannten "Keil im Keil-Prinzip" spreizbar. Unterhalb bzw. neben der Schieberplatte 16 ist eine Rohrbrücke 23 angeordnet, die sich aus zwei Dichtringen 24, 25 sowie einem die Dichtringe miteinander verbindenden Kompensator 26 zusammensetzt. Der Kompensator 26 besteht aus einem inneren Rohrabschnitt 27 und einem sich koaxial dazu erstreckenden äußeren Rohrabschnitt 28, wobei der äußere Rohrabschnitt 28 mit beiden Dichtringen 24, 25 fest verbunden ist, nämlich verschweißt (Ringschweißnähte 29, 30) und eine sich über den Umfang erstreckende Welle bzw. Einbuchtung 31 aufweist. Der innere Rohrabschnitt 27 ist dagegen hohlzylindrisch, d. h. ohne Wellung ausgebildet, so daß keine dadurch bedingten Strömungsverluste auftreten. Des weiteren ist der innere Rohrabschnitt nur mit einem der beiden Dichtringe, nämlich hier dem Dichtring 25, fest verbunden (Ringschweißnaht 32). Gegenüber dem anderen Dichtring 24 ist der innere Rohrabschnitt 27 axial bewegbar, wobei das Axialspiel zwischen dem Dichtring 24 und dem inneren Rohrabschnitt 27 zwischen etwa 1,0 mm bis etwa 5,0 mm liegt. Die Anordnung des inneren Rohrabschnitts 26 gegenüber den beiden Dichtringen 24 und 25 ist so, daß die Innenfläche des Rohrabschnitts 26 mit den Innenflächen der Dichtringe 24 und 25 jeweils fluchtet, so daß ein praktisch ununterbrochener Strömungsdurchgang in Offenstellung des Schiebers geschaffen ist. In den Fig. 1 und 2 ist der Schieber in Schließstellung dargestellt. Das Schiebergehäuse 11 ist nach außen hin fluiddicht ausgebildet, so daß innerhalb des Schiebergehäuses bzw. im Innern 33 desselben ein Gasdruck einstellbar ist, der größer ist als der Druck im Schieberdurchgang bzw. in der in den Fig. 1 und 2 nicht dargestellten Rohrleitung bei Schieberoffenstellung. Demnach muß auch die Betätigungsstange 22 fluiddicht in das Schiebergehäuse 11 eingeführt sein. Am Schiebergehäuse 11 ist ein Anschluß 34 zur Verbindung mit einer nicht dargestellten Druckgasquelle, insbesondere Spüldampfquelle, angeordnet. Bei der in den Fig. 1 und 2 dargestellten Ausführungsform sind die Dichtflachen der Dichtringe 24, 25 einerseits und Gehäusedichtsitze 14, 15 andererseits jeweils sich parallel zur Schieberbetätigungsrichtung erstreckend ausgebildet, und zwar in an sich bekannter Weise gehärtet bzw. gepanzert, um die Verschleißfestigkeit zu erhöhen.1 and 2 has a
Des weiteren erstreckt sich die umlaufende Einbuchtung 31 des äußeren Rohrabschnitts 28 bis nahe zur Außenfläche des inneren Rohrabschnitts 27 hin, so daß der im Gehäuseinnern 33 herrschende Gasdruck über die umlaufende Einbuchtung 31 auf die Dichtringe 24, 25 unter axialer Spreizung derselben voll wirksam ist. Die axiale Spreizung der Dichtringe 24, 25 ist zum einen durch die umlaufende Einbuchtung 31 und zum anderen durch das Axialspiel zwischen dem inneren Rohrabschnitt 27 und einem der beiden Dichtringe, hier Dichtring 24, möglich.Furthermore, the
Die Rohrbrücke 23 wird demnach durch die beiden Dichtringe 24, 25 einerseits und die zwischen diesen angeordneten, als Kompensator 26 dienenden inneren und äußeren Rohrabschnitte 27, 28 andererseits unter Ausbildung eines Ringkastens 35 begrenzt. Dieser Ringkasten 35 bzw. der Ringraum zwischen innerem und äußerem Rohrabschnitt 27 und 28 ist mit einem wärmeisolierenden Material, insbesondere Glaswolle, Steinwolle, oder dgl., ausgefüllt. Diese Ausfüllung hat nicht nur einen wärmeisolierenden Zweck, sondern auch den Zweck, das Eindringen von Strömungsmedium in den genannten Ringraum zwischen innerem und äußerem Rohrabschnitt zu verhindern. Ein Zusetzen des Ringraums mit Strömungsmedium oder bei Gasströmung mit Staub- und Schmutzpartikeln oder dgl. Ablagerungen würde nach längerem Gebrauch die Wirkung des Kompensators 26 empfindlich stören bzw. beeinträchtigen. Insofern hat die vorgenannte Ausfüllung eine Doppelfunktion.The
Da alle übrigen Konstruktionsdetails des in den Fig. 1 und 2 dargestellten Doppelplattenschiebers an sich bekannt sind, erübrigt sich hier eine nähere Beschreibung dieser Teile, zumal diese ohnehin außerhalb des hier fraglichen Erfindungsgedankens liegen.Since all other construction details of the double-plate slide shown in FIGS. 1 and 2 are known per se, a detailed description of these parts is unnecessary here, especially since they are anyway outside the inventive concept in question here.
Grundsätzlich ist es noch denkbar, dem Schiebergehäuse 11 bzw. dem Innenraum 33 desselben ein einstellbares Druckbegrenzungsventil zuzuordnen, um einen vorbestimmten Druck im Innern 33 des Schiebergehäuses 11 nicht zu übersteigen, wobei dieser Druck so eingestellt ist, daß er eine ausreichend hohe Dichtsicherheit zwischen den Dichtringen 24, 25 einerseits und den zugeordneten Gehäusedichtsitzen 14, 15 des Schiebergehäuses andererseits bei Schieberoffenstellung gewährleistet.Basically, it is still conceivable to assign an adjustable pressure relief valve to the
Bei der dargestellten Ausführungsform ist im übrigen auch noch zu bedenken, daß im Ringraum zwischen innerem und äußerem Rohrabschnitt in der Praxis ein etwas geringerer Druck herrschen wird als im Schieberdurchgang bzw. in der Rohrleitung, und zwar bedingt durch die Drosselstelle im Axialspielbereich zwischen dem Dichtring 24 und dem inneren Rohrabschnitt 27 und/oder bei etwas höherer Strömungsgeschwindigkeit im Schieberdurchgang bzw. in der Rohrleitung, bedingt durch den dabei entstehenden "Wasserpumpen-Effekt" . Die Folge ist, daß der im Innern 33 des Schiebergehäuses 11 herrschende Überdruck noch wirksamer auf die beiden Dichtringe 24, 25 unter axialer Spreizung derselben einwirken kann.In the embodiment shown, it should also be borne in mind that, in practice, a somewhat lower pressure in the annular space between the inner and outer tube section will prevail as in the slide passage or in the pipe, due to the throttle point in the axial play area between the sealing
In den Fig. 3 und 4 sind noch Abwandlungen der Erfindung entsprechend Anspruch 7 im schematischen Teilschnitt dargestellt, wobei jeweils mit der Bezugsziffer 27 der innere Rohrabschnitt, mit 28 der äußere Rohrabschnitt, mit 24,25 die beiden Dichtringe, mit 33 das unter Gasüberdruck stehende Innere des Schiebergehäuses 11, mit 36 ringförmige Einsätze aus Panzerstahl oder dgl. sowie mit 29,30,32 Ringschweißnähte bezeichnet sind. Die schiebergehäuseseitig axial einander zugewandten Flächen von Dichtringen sowie äußerem Rohrabschnitt (Fig. 3) sind mit dem Bezugszeichen 37 gekennzeichnet. Diese sind bei Überdruck im Schiebergehäuse 33 wirksam derart, daß eine axiale Spreizung des äußeren Rohrabschnitts 28 unter Abdichtung im Bereich der Ringeinsätze 36 erfolgt. Bei der Ausführungsform nach Fig. 4 erfolgt die abdichtende Verbindung zwischen dem äußeren, glatten Rohrabschnitt und dem unteren Dichtring 24 über einen Ringwulst, der eine axiale Relativbewegung zwischen den beiden Dichtringen 24, 25 unter den vorbeschriebenen Bedingungen erlaubt.3 and 4 modifications of the invention according to claim 7 are shown in a schematic partial section, the
Claims (9)
- A double-plate slide valve comprising a slide plate (16) which can be displaced by virtue of an actuating rod (22) and is provided with a tube bridge (23) which comprises two sealing rings (24, 25) which are interconnected by virtue of a compensator (26), which sealing rings can be pressed whilst being elastically prestressed against the sealing ring seat (14, 15) of the slide valve housing (11) when the slide valve (10) is in the open position, wherein the compensator (26) is formed in a fluid-tight manner between the two sealing rings (24, 25) and includes an elastically resilient tube portion which is curved in a wave-like manner and includes a recess (31) which extends over the periphery, characterised in that the wave-like curved tube portion extends as the outer tube portion (28) in a coaxial manner over an inner tube portion (27) which is fixedly connected to only one (25) of the two sealing rings (24, 25), whereas it can move in an axial direction with respect to the other sealing ring (24) and that in the inside (33) of the slide valve housing (11) a gas pressure, which serves to press down the sealing rings (24, 25), can be adjusted, which gas pressure is greater than the pressure in the slide valve through passage when the slide valve is in the open position.
- A slide valve according to claim 1, characterised in that the annular chamber (35) between the inner (27) and the outer (28) tube portion is filled with a heat-insulation material, in particular glass wool, rock wool etc.
- A slide valve according to claim 1 or 2, characterised in that the actuating rod (22) is guided into the slide valve housing (11) in a fluid-tight manner and that for the purpose of connecting a pressure gas source, in particular a scavenging steam source, a connection (34) is disposed on the slide valve housing (11).
- A slide valve according to any one of claims 1 to 3, characterised in that the sealing surfaces of the sealing rings (24, 25) on the one hand and of the associated housing sealing ring seats (14, 15) on the other hand extend in each case parallel with the slide actuating direction and perpendicular to the slide valve through passage longitudinal axis.
- A slide valve according to any one of claims 1 to 4, characterised in that the circumferential recess (31) of the outer tube portion (28) extends approximately to the outer surface of the inner tube portion (27).
- A slide valve according to any one of claims 1 to 5, characterised in that the tube bridge (23) is defined on the one side by the two sealing rings (24, 25) and on the other side by the inner and outer tube portions (27, 28) which are disposed between the said sealing rings and serve as a compensator (26), wherein the inner surface of the inner tube portion (27) is aligned and flush with the inner surfaces of the two sealing rings (24, 25).
- A double-plate slide valve comprising a slide plate (16) which can be displaced by virtue of an actuating rod (22) and is provided with a tube bridge (23) which comprises two sealing rings (24, 25) which are interconnected by virtue of a compensator (26), which sealing rings can be pressed whilst being elastically prestressed against the sealing ring seat (14, 15) of the slide valve housing (11) when the slide valve (10) is in the open position, wherein the compensator (26) is formed in a fluid-tight manner between the two sealing rings (24, 25) and includes a tube portion which is elastically resilient in the axial direction, characterised in that the elastically resilient tube portion extends as the outer tube portion (28) in a coaxial manner over an inner tube portion (27), which is fixedly connected to only one (25) of the two sealing rings (24, 25) whereas it can move in an axial direction with respect to the other sealing ring (24), wherein the total of the surfaces facing each other in an axial direction of the tube portion and of the sealing rings (24, 25) and outer tube portion (28) is greater than the total of the surfaces facing away from each other in the axial direction of the tube portion and that in the inside (33) of the slide valve housing (11) a gas pressure, which serves to press down the sealing rings (24, 25) can be adjusted, which gas pressure is greater than the pressure in the slide valve through passage when the slide valve is in the open position.
- A slide valve according to any claims 1 to 7, characterised in that the sealing surfaces of the two sealing rings (24, 25) are formed or rather are effective in each case along the outer periphery thereof.
- A slide valve according to claim 8, characterised in that the sealing surfaces of the sealing ring (24, 25) are formed by virtue of inserts (35) which extend along the outer periphery thereof and are made of hardened steel.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4011274A DE4011274C1 (en) | 1990-04-06 | 1990-04-06 | |
| DE4011274 | 1990-04-06 |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| EP0450646A2 EP0450646A2 (en) | 1991-10-09 |
| EP0450646A3 EP0450646A3 (en) | 1992-03-04 |
| EP0450646B1 true EP0450646B1 (en) | 1995-07-05 |
Family
ID=6403964
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP91105416A Expired - Lifetime EP0450646B1 (en) | 1990-04-06 | 1991-04-05 | Double plate gate valve |
Country Status (9)
| Country | Link |
|---|---|
| US (1) | US5116022A (en) |
| EP (1) | EP0450646B1 (en) |
| AT (1) | ATE124766T1 (en) |
| BR (1) | BR9101398A (en) |
| CA (1) | CA2039641C (en) |
| DE (2) | DE4011274C1 (en) |
| ES (1) | ES2077099T3 (en) |
| RU (1) | RU2050494C1 (en) |
| ZA (1) | ZA912537B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1998017934A1 (en) * | 1996-10-23 | 1998-04-30 | Zimmermann & Jansen Gmbh | Slider, especially a pipe bridge slider |
Families Citing this family (46)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4414176A1 (en) * | 1994-04-22 | 1995-10-26 | Zimmermann & Jansen Gmbh | Knife gate valve |
| DE4422055C1 (en) * | 1994-06-23 | 1995-12-07 | Zimmermann & Jansen Gmbh | Device for actuating an arrangement of guide tube slides |
| DE19723962C2 (en) * | 1997-06-06 | 2000-05-31 | Zimmermann & Jansen Gmbh | Double knife gate valve |
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| US7086416B2 (en) * | 2004-05-27 | 2006-08-08 | Zimmerman & Jansen, Inc. | Valve assembly having a compensating gate |
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| US8440057B2 (en) * | 2008-01-23 | 2013-05-14 | Curtiss-Wright Flow Control Corporation | Linked coke drum support |
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| DE102009017634A1 (en) | 2009-04-16 | 2011-03-31 | Z & J Technologies Gmbh | Double knife gate |
| US8459608B2 (en) | 2009-07-31 | 2013-06-11 | Curtiss-Wright Flow Control Corporation | Seat and valve systems for use in delayed coker system |
| CN101709807B (en) * | 2009-12-04 | 2012-03-21 | 沈阳东北电力调节技术有限公司 | Linear-direction compensator |
| TWI448635B (en) * | 2010-04-14 | 2014-08-11 | Wue Shyang Machinery Co Ltd | Two-way control valve |
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| DE202016102554U1 (en) | 2016-01-29 | 2016-06-21 | Z & J Technologies Gmbh | Double plate gate valve for an ethylene plant and ethylene plant |
| DE202016102559U1 (en) | 2016-01-29 | 2016-06-20 | Z & J Technologies Gmbh | Double plate gate valve for an ethylene plant and ethylene plant |
| DE102016111169B4 (en) * | 2016-06-17 | 2019-04-25 | ZMK Technologies GmbH | Valve with erosion protection device |
| EP3306150A1 (en) | 2016-10-04 | 2018-04-11 | Paul Wurth S.A. | Gate valve for a chemical plant |
| DE102018101472A1 (en) | 2018-01-23 | 2019-07-25 | Z & J Technologies Gmbh | Slide valve and use of a slide valve |
| CN108757973B (en) * | 2018-08-16 | 2023-11-14 | 北京航天石化技术装备工程有限公司 | Double-flashboard gate valve |
| CN109373003B (en) * | 2018-11-30 | 2023-08-22 | 洛阳三旋智能装备有限公司 | Electric single-screw gas-assisted sealed coke tower top valve |
| CN112161071B (en) * | 2020-08-20 | 2022-09-30 | 山东中车华腾环保科技有限公司 | Electric slide valve and train excrement collecting system comprising same |
| DE102022105939A1 (en) | 2021-07-14 | 2023-01-19 | Z & J Technologies Gmbh | Knife gate valve, method of operation and use |
| WO2023285506A1 (en) | 2021-07-14 | 2023-01-19 | Z & J Technologies Gmbh | Slide gate valve, operating method and use |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2306490A (en) * | 1939-09-11 | 1942-12-29 | Reed Roller Bit Co | Valve |
| DE868543C (en) * | 1951-02-27 | 1953-02-26 | Heinz Bechler | Gate valve with a tight draft tube |
| US2705610A (en) * | 1951-05-05 | 1955-04-05 | Crane Co | Conduit valve |
| FR2054522B1 (en) * | 1969-07-30 | 1973-05-11 | Guichon Robert | |
| DE2713149A1 (en) * | 1977-03-25 | 1978-09-28 | Zimmermann & Jansen Gmbh | Slider valve for pneumatic pipeline - has tubular bridge sleeve and circular shut=off plate operated by screw spindle |
| US4244557A (en) * | 1977-10-07 | 1981-01-13 | Leybold-Heraeus Gmbh | High vacuum seal |
| DE2745139A1 (en) * | 1977-10-07 | 1979-04-12 | Leybold Heraeus Gmbh & Co Kg | Slide valve high vacuum seal - has valve seat fitted in pipe section in which valve plate periphery is guided |
| DE8008316U1 (en) * | 1980-03-26 | 1980-07-17 | Hermann Rappold & Co Gmbh, 5160 Dueren | DOUBLE RECEIVER WITH PIPE BRIDGE |
| DD233402A5 (en) * | 1985-04-19 | 1986-02-26 | Jakovic,Mladen,Ch | WEDGE SLIDE |
-
1990
- 1990-04-06 DE DE4011274A patent/DE4011274C1/de not_active Expired - Lifetime
-
1991
- 1991-04-03 CA CA002039641A patent/CA2039641C/en not_active Expired - Lifetime
- 1991-04-03 US US07/679,783 patent/US5116022A/en not_active Expired - Lifetime
- 1991-04-05 AT AT91105416T patent/ATE124766T1/en not_active IP Right Cessation
- 1991-04-05 DE DE59105898T patent/DE59105898D1/en not_active Expired - Lifetime
- 1991-04-05 EP EP91105416A patent/EP0450646B1/en not_active Expired - Lifetime
- 1991-04-05 ES ES91105416T patent/ES2077099T3/en not_active Expired - Lifetime
- 1991-04-05 ZA ZA912537A patent/ZA912537B/en unknown
- 1991-04-05 RU SU914895134A patent/RU2050494C1/en active
- 1991-04-08 BR BR919101398A patent/BR9101398A/en not_active IP Right Cessation
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1998017934A1 (en) * | 1996-10-23 | 1998-04-30 | Zimmermann & Jansen Gmbh | Slider, especially a pipe bridge slider |
Also Published As
| Publication number | Publication date |
|---|---|
| US5116022A (en) | 1992-05-26 |
| DE59105898D1 (en) | 1995-08-10 |
| CA2039641A1 (en) | 1991-10-07 |
| EP0450646A2 (en) | 1991-10-09 |
| ZA912537B (en) | 1991-12-24 |
| RU2050494C1 (en) | 1995-12-20 |
| DE4011274C1 (en) | 1991-08-01 |
| ATE124766T1 (en) | 1995-07-15 |
| CA2039641C (en) | 1994-11-08 |
| ES2077099T3 (en) | 1995-11-16 |
| EP0450646A3 (en) | 1992-03-04 |
| BR9101398A (en) | 1991-11-26 |
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